EP2642147B1 - Embrayage à friction - Google Patents

Embrayage à friction Download PDF

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Publication number
EP2642147B1
EP2642147B1 EP13001143.0A EP13001143A EP2642147B1 EP 2642147 B1 EP2642147 B1 EP 2642147B1 EP 13001143 A EP13001143 A EP 13001143A EP 2642147 B1 EP2642147 B1 EP 2642147B1
Authority
EP
European Patent Office
Prior art keywords
lever
friction
spring
friction element
pressure plate
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP13001143.0A
Other languages
German (de)
English (en)
Other versions
EP2642147A1 (fr
Inventor
Marc Finkenzeller
Michael Schneider
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP2642147A1 publication Critical patent/EP2642147A1/fr
Application granted granted Critical
Publication of EP2642147B1 publication Critical patent/EP2642147B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/583—Diaphragm-springs, e.g. Belleville
    • F16D13/585—Arrangements or details relating to the mounting or support of the diaphragm on the clutch on the clutch cover or the pressure plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/22—Vibration damping

Definitions

  • the invention relates to a friction clutch, which can be used in particular as a starting clutch in a drive train of a motor vehicle and with the aid of which torque from an input shaft, for example a crankshaft of an engine, on an output shaft, for example, an input shaft of a transmission, can be forwarded.
  • a torque generated by a motor vehicle engine can be transmitted via a flywheel rotatable about an axis of rotation. With the flywheel a pressure plate for forwarding the torque is connected, which can then transmit the torque via a friction lining to a clutch disc frictionally.
  • An object of the invention is therefore to provide a friction clutch for a drive train of a vehicle, with the aid of an improved torque transmission when closing the clutch is enabled and less Anfahrrattern occurs, without significantly reducing Anfahr nie.
  • a friction clutch for a drive train of a motor vehicle, with a pressure plate, the rotationally fixed, but axially limited displaceable with a Coupling housing is connected to a preferably designed as a plate spring lever spring for applying force to the pressure plate in the axial direction to clamp a clutch disc between the pressure plate and a counter plate and a damping device with at least one friction element for damping axial vibrations of the pressure plate and / or the lever spring relative to the housing.
  • the at least one friction element has at least one contact region which is in operative connection with the pressure plate and / or with the lever spring and / or with the housing only over a part a of the lever travel of the lever spring.
  • the operative connection is an operative connection between contact area and pressure plate and / or lever spring.
  • the operative connection is an operative connection between the contact region and the housing, in particular the housing cover. Due to the configuration and arrangement of the friction element, in particular the at least one contact region of the friction element, and the housing or the lever spring or the pressure plate is ensured that said friction region with the housing, the pressure plate and / or with the lever spring only over part of the Hebelwegs operatively engaged.
  • the operative intervention takes place in particular via a frictional connection.
  • this increase in hysteresis takes place only over a part of the lever travel, namely the said part a of the lever travel or the release travel.
  • the active connection is based on force or friction fit.
  • the friction clutch is preferably designed as a starting clutch for forwarding a torque from a crankshaft of an engine of the motor vehicle to an input shaft of a transmission of the motor vehicle.
  • the hysteresis of the clutch in particular the release force hysteresis, can be increased within a predetermined range and thus the starting chatter can be reduced or suppressed.
  • the damping device has a plurality of the friction elements and these can be distributed substantially uniformly about an axis of rotation of the clutch, in order to distribute their effect on the hysteresis of the clutch also largely uniform.
  • the at least one friction element with the housing in particular with the housing cover, connected and it comes on the part a of the lever travel of the lever spring to an operative connection between the contact area and pressure plate and / or lever spring.
  • Particularly advantageous is the alternative, in which it comes on the part a of the lever travel of the lever spring to an operative connection between the contact area and the lever spring.
  • the at least one friction element is adapted to abut in its contact region with bias on the pressure plate and / or on the lever spring and / or on the housing and from a predetermined position on the lever or Ausgurweg (preferably on End of the aforementioned part a of the lever travel) of the pressure plate and / or the lever spring to solve or remove.
  • the at least one friction element bears against the contact area with prestress against the pressure plate and / or on the lever spring and / or on the housing and from a predetermined position on the lever or Ausschreibweg of the pressure plate and / or released from the lever spring.
  • the predetermined position is at the end of the one part a of the lever travel.
  • At least one friction element is designed as a bolt and / or tab and engages between two plate spring tongues of the diaphragm spring, wherein the at least one contact region is formed on the flanks of the bolt or the tab.
  • the at least one bolt and / or the at least one tab engages / engage finger-like in the space or the spaces between the plate spring tongues designed as a plate spring lever spring.
  • the contour of the formed as a bolt and / or tab friction element tapers in at least a portion of its longitudinal axis. At the tapered point, the contour is narrower than the distance between the corresponding plate spring tongues.
  • the friction element is resilient. If the friction element is designed, for example, as a tab or bracket, then the resilient embodiment is a bending-resilient design of the friction element.
  • the at least one friction element is adapted to be biased axially over the part a of the lever travel to press on the lever spring.
  • the at least one friction element presses axially over the part a of the lever travel onto the lever spring.
  • the at least one friction element of the damping device in the contact region is bow-shaped or wavy.
  • the at least one friction element in the contact region has a treated surface, preferably treated by coating and / or by roughening.
  • the hysteresis of the clutch system according to the invention in particular the Ausschkrafthysterese be increased and by this targeted increase in the hysteresis of the clutch system (ie, the higher damping), the torque fluctuations can be reduced and thus the Rattergehoffsche be eliminated.
  • the hysteresis can also be increased by increasing the coefficient of friction at the contact points of the pressure plate disk spring, disk spring wire ring, disk spring centering pin / centering plate, disc spring release bearing.
  • FIGS. 1 to 3 each show a part of a friction clutch 10.
  • the friction clutch 10 is in particular a clutch 10 with a path-controlled wear adjustment.
  • the friction clutch 10 which is designed in particular for use as a starting clutch in a drive train of a motor vehicle, has a pressure plate 12 which is non-rotatably, but limitedly displaceable in the axial direction A connected to a clutch housing 14.
  • the coupling 10 has a lever spring designed as a plate spring 18, which is effective as a contact pressure between the pressure plate 12 and the housing 14 and the pressure plate 12 in the axial direction A (ie in the FIGS. 1 to 3 down) is urged to pinch a clutch plate (not shown) between the pressure plate 12 and a backing plate (not shown).
  • the lever spring designed as a plate spring 18 presses in the radially outer region 20 against an opening provided on the pressure plate 12 adjusting ring 22 which is opposite a spacer bolt (not shown) in the housing cover 14.
  • the radially outer portion 20 of the plate spring 18 is annular and the individual plate spring tongues 24 of the plate spring 18 extend from the annular outer portion 20 radially inwardly.
  • the lever spring 18 can be actuated by means of a lever, not shown. If the lever spring 18 is not actuated, this results in the position of the spring 18 shown by solid lines. In this position, the spring 18 presses the pressure plate 12 in the axial direction A against the (not shown) counter plate and presses the clutch disc. The clutch 10 is closed.
  • the spring 18 Upon actuation of the clutch 10, the spring 18 is moved in the central region 24 in the axial direction A, which in turn by means of a pivot bearing 28 with a wire ring 30 (or (cup spring) bolt 32, as in Fig. 2 shown) causes an axial movement of the pressure plate 12.
  • the clutch 10 further comprises a damping device 32 with a plurality of friction elements 34, which are distributed substantially uniformly around an outer periphery of the pressure plate 12.
  • a damping device 32 with a plurality of friction elements 34, which are distributed substantially uniformly around an outer periphery of the pressure plate 12.
  • Each of the friction elements 34 in this embodiment is formed as a tab 36 (preferably made of sheet metal), more precisely as a centering, which has contact areas 38 on its flanks for an operative connection with the plate spring tongues 40 of the plate spring 18.
  • a 90 ° angle On the right side of the Fig. 1 This situation is shown by a 90 ° angle. It can be clearly seen how the friction element formed as a tab 36 34 is in operative connection with the associated plate spring tongues 40 in a first part a of the lever travel.
  • the friction element 34 may also be formed as bulbous plate / lever spring bolt 30, the bulbous portion 44 only in a limited tilting range of the plate spring / lever spring 18 with the plate spring / lever spring 18th has increased friction.
  • FIG. 2 is a friction clutch 10 according to a second embodiment shown schematically in partial view. Since this embodiment is substantially the same FIG. 1 corresponds, should be discussed here only on the differences.
  • the embodiment of the Fig. 2 differs by the structure of the damping device 32 of the embodiment of Fig. 1 , Also in Fig. 2 shown damping device 32 has at least one friction element 34. However, the friction member 34 is formed as the disc spring pin 32 for centering the plate spring 18.
  • the bolt 32 is formed bulbous in the section 44. This bulbous portion 44 forms the contact portions 38 of the friction element 34. On the right side of the Fig. 2 is the bulbous portion 44 on the bolt 30 shown in detail.
  • the spring 18 Upon actuation of the clutch 10, the spring 18 is moved in the central region 24 in the axial direction A, which in turn by means of a pivot bearing 28 with a wire ring 30 (or (cup spring) bolt 32, as in Fig. 2 shown) causes an axial movement of the pressure plate 12.
  • Each of the friction elements 34 in this embodiment serves as a centering pin 30. It is clearly visible how the formed as a bolt 30 friction member 34 is in the first part a of the lever travel by means of its bulbous portion 44 in operative connection with the associated plate spring tongues 40. There is an increased coefficient of friction between the attached to the housing 14 friction member 34 and the lever spring 18 in this part a of the lever or Ausschreibwegs. The in the Fig. 4 shown Ausgurkrafthysterese is additionally increased in the part a of the Ausschreibwegs shown due to this increased coefficient of friction (dashed lines).
  • FIG. 3 is a friction clutch 10 according to a third embodiment shown schematically in partial view. Since this embodiment essentially those of Figures 1 and 2 corresponds, should be discussed here only on the differences.
  • the embodiment of the Fig. 3 differs by the structure of the damping device 32 of the embodiment of Fig. 1 , Also in Fig. 3 shown damping device 32 has at least one friction element 34.
  • the friction element 34 is formed as a spring clip 46 which is resilient and biased over the part a of the lever travel axially presses on the lever spring 18.
  • the contact portion 38 of this designed as a spring clip 46 friction element 34 in part a of the lever travel with bias to the lever spring 18 and dissolves from the end position of this part a of the lever travel (or Ausschwegs) of the lever spring 18.
  • Ausgurkrafthysterese illustrated in the part a of the Ausgurwegs shown due to this increased coefficient of friction additionally increased (in Fig. 4 dashed lines drawn) while the subsequent part of the lever or Ausschwegs s is not additionally increased.
  • FIG. 4 shows - as mentioned - the resulting Ausgurkrafthysterese.
  • two Ausschreibkraftkennlinien 48 (solid line) and 50 (dashed line) are shown as a graph in a force (F) -Weg (s) representation.
  • the Ausschreibkraftkennline 48 shows the situation without damping device 32. It results in a hysteresis with characteristic opening on the lever or Ausschreibweg s. Due to the increased coefficient of friction at the contact points pressure plate-plate spring, plate spring wire ring, disc spring centering / centering and / or disc spring release bearing, the opening of the hysteresis in part a of the lever or Ausschreibwegs s is increased (dashed lines Ausschreibkraftkennlinien 50). In the further part of the lever or Ausschreibwegs s fall the two curves 48, 50 to each other.
  • the at least one friction element 34 advantageously has a friction-increasing coating (eg polyamide) and / or a roughened surface (eg by blasting).
  • a friction-increasing coating eg polyamide
  • a roughened surface eg by blasting
  • the use of lubricants can be dispensed with in the contact areas 38.
  • the friction elements 34 may be wavy or bow-shaped. It is also possible to form the plate spring 18 in multiple layers.
  • the described modulation of the hysteresis can be achieved both with simple couplings 10 and with couplings with wear adjustment by means of such a damping device 32 with friction elements 34.
  • the friction elements 34 are formed and / or arranged such that the increase of the hysteresis takes place only in a limited release region (part a).
  • a release of the frictional engagement (as an operative connection) between the respective friction element 34 and the disc spring / lever spring 18 takes place after this release region.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Claims (8)

  1. Embrayage à friction (10) pour une chaîne cinématique d'un véhicule automobile, comprenant une plaque de pressage (12) qui est connectée de manière solidaire en rotation mais de manière déplaçable axialement dans une mesure limitée à un boîtier d'embrayage (14), en particulier un couvercle de boîtier (16),
    un ressort de levier (18) pour la sollicitation par force de la plaque de pressage (12) dans la direction axiale (A), de manière à serrer un disque d'embrayage entre la plaque de pressage (12) et une plaque conjuguée, et
    un dispositif d'amortissement (32) comprenant au moins un élément de friction (34) pour l'amortissement des oscillations axiales de la plaque de pressage (12) et/ou du ressort de levier (18) par rapport au boîtier (16),
    l'au moins un élément de friction (34) présentant au moins une région de contact (38) qui est en liaison fonctionnelle uniquement sur une partie (a) de la course de levier du ressort de levier (18) avec la plaque de pressage (12) et/ou avec le ressort de levier (18) et/ou avec le boîtier (16), caractérisé en ce que
    l'au moins un élément de friction (34) est réalisé sous forme de boulon (30) et/ou de patte (36) et vient en prise entre deux langues (40) du ressort de levier (18), l'au moins une région de contact (38) étant réalisée au niveau des flancs du boulon (30) et/ou de la patte (36).
  2. Embrayage à friction selon la revendication 1, dans lequel l'au moins un élément de friction (34) est prévu pour s'appliquer dans sa région de contact (38) avec précontrainte contre la plaque de pressage (12) et/ou le ressort de levier (18) et/ou le boîtier (16) et pour se détacher, à partir d'une position prédéterminée sur la course de levier, de la plaque de pressage (12) et/ou du ressort de levier (18) et/ou du boîtier (16).
  3. Embrayage à friction selon la revendication 1 ou 2, dans lequel le contour de l'élément de friction (34) réalisé sous forme de boulon (30) et/ou de patte (36) se rétrécit dans au moins une région de son axe longitudinal.
  4. Embrayage à friction selon l'une quelconque des revendications 1 à 3, dans lequel l'élément de friction (34) réalisé sous forme de boulon (30) et/ou de patte (36) s'engage seulement sur une partie (a) de la course de levier dans l'espace intermédiaire entre les deux langues (40).
  5. Embrayage à friction selon l'une quelconque des revendications 1 à 4, dans lequel l'élément de friction (34) est réalisé de manière élastique.
  6. Embrayage à friction selon l'une quelconque des revendications 1 à 5, dans lequel l'au moins un élément de friction (34) presse axialement sur le ressort de levier (18) de manière précontrainte sur la partie (a) de la course de levier.
  7. Embrayage à friction selon l'une quelconque des revendications 1 à 6, dans lequel l'au moins un élément de friction (34) du dispositif d'amortissement (32) est réalisé en forme d'étrier ou en forme ondulée dans la région de contact (38).
  8. Embrayage à friction selon l'une quelconque des revendications 1 à 7, dans lequel l'au moins un élément de friction (34) présente dans la région de contact (38) une surface traitée, de préférence traitée par revêtement et/ou par grainage.
EP13001143.0A 2012-03-23 2013-03-07 Embrayage à friction Not-in-force EP2642147B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012204692 2012-03-23

Publications (2)

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EP2642147A1 EP2642147A1 (fr) 2013-09-25
EP2642147B1 true EP2642147B1 (fr) 2017-01-04

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP13001143.0A Not-in-force EP2642147B1 (fr) 2012-03-23 2013-03-07 Embrayage à friction

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EP (1) EP2642147B1 (fr)
DE (1) DE102013203785A1 (fr)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19647974B4 (de) * 1995-12-05 2012-01-26 Schaeffler Technologies Gmbh & Co. Kg Reibungskupplung
DE19746281B4 (de) 1996-10-24 2007-10-04 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Reibungskupplung
DE10322783B4 (de) * 2002-06-19 2013-10-31 Zf Friedrichshafen Ag Reibungskupplung mit Reibungsdämpfungsvorrichtung
DE102009020289A1 (de) * 2009-05-07 2010-11-11 Zf Friedrichshafen Ag Druckplattenbaugruppe für eine Reibungskupplung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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Publication number Publication date
DE102013203785A1 (de) 2013-09-26
EP2642147A1 (fr) 2013-09-25

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